Valve construction



Aug. 29, 1933. E. J. svENsoN VALVE CONSTRUCTION Filed Nov. v16. 192s 4 Sheets-Sheet l- QN) NQN Aug. 29,- 1933. E. J. svENsoN VALVE CONSTRUCTION Filed Nov. 16, 1929 4 Sheets-Sheet 2 N @o Q @QN o v 1 @5N M w NQN Yau www1 .J @QH O QN ew @my SN Aug. 29, 1933. E, J; svENsoN 1,924,422

VALVE CONSTRUCTION 2 Filed Nov. 16, 1929 4 Sheets-Sheet 3 l 66 2Q-6 @W32 1w 466@ j@ lwn Aug. 29, 1933. E. J. svl-:NsoN 1,924,422

VALVE CONSTRUCTION l Filed- Nov. 16, 1929 4 Sheets-Sheet 4 CTI (Patented Aug. 29, 1933 UNITED STATESy VALVE CONSTRUCTION Ernest J. Svenson, Rockford, l'll.

Application November 16, 1929 Serial No. 407,781

43 Claims.

My present invention relates generally to fluid control mechanisms and more particularly to valves for automatically controlling the distribution cffluid which is used as a propelling medium.

In general, one of the primary objects of this invention is to provide a valve of improved practical and simple construction which is adapted to efficiently and automatically control the distribution of high pressure and low pressure fluids.

More specifically, it isan object of my present invention to provide a unique valve arrangement for accurately and positively controlling the distribution of high and low pressure fluids to a plurality of fluid operated actuating mechanisms as for example those mechanisms used for effecting the actuationpf machine elements.

Another object is to provide an improved fluid valve construction which will preclude the necessity of employing any auxiliary devices for controlling or effecting the reversal of the valve and to this end I propose to provide a self-contained valve unit which may be shifted in response to the action of the fluid medium.

Another object of my present invention is to provide a valve mechanism which will enable the combining of fluids under low and high pressures to permit increased displacement of said fluid for high speed transmission. 'V

Still more specifically, my present invention contemplates the provision of a novel fluid valve arrangement in which a valve unitwithin a housing may be shifted by unbalancing the fluid pressure on said valve, said unbalancing being occasioned in response to the displacement of fluid from the valve chamber.

Still another object of the present invention is to provide a self-contained valve mechanism which may be effectively employed for distributing fluid to a plurality of fluid actuated mechanisms and to this end I propose to provide a plurality of adjustable and non-adjustable orifices which are` directly associated with the valve unit, said orifices serving to direct fluid tosaid actuating mechanisms.

' It is also an object of my present invention to provide a valve mechanism of the above mentioned improved construction which may be manually or automatically actuated and in this connection I contemplate `the provision Y of simple means whereby certain of the automatic controlling devices may be rendered inoperative to effect complete manual control of the main valve unit.

These and numerous other objects and advantages will be more apparent from the detailed description which is to follow. In accordance with the general features of the invention, one embodiment thereof includes a main cylindrical valve Jwhich is longitudinally slidable Within a housing. One extremity of this valve is adapted to be connected to a control lever whereby manual reposite extremity of the valve chamber.

source of high pressure and low pressure fluid supply. When the control lever is shifted to an .extreme position as for example to the left, ports within the valve unit are so positioned as to cause the high'and low pressure fluids to be directed through properly gaged, fixed passages to the machine actuating mechanisms. This rapid displacement of the fluid causes said'mechanisms to be actuated at high speed. Thus, if these mechanisms were used for moving machine tools, said tools would be caused to rapidly move into operative association with the work. This movement might be referred to as a rapid approach movement. At a predetermined stage of the operation of these fluid actuated mechanisms, the main valve is automatically or manually shifted to a position in which only the high pressure fluid is directed to the machine actuating mechanisms and at this time said fluid is directed to restricted or adjustable orifices associated directly with the housing of the main valve. The reason forl employing these adjustable restricted oriflces will be apparent when it is understood that a variable amount of fluid must be displaced to give the desired speed .to the parts which are propelled by the fluid actuated mechanisms. That is, the speed of these parts or members is controlled by means of these adjustable orices. In other Words, the fluid is now displaced at a feeding rate to the actuating mechanisms. At a subsequent predetermined interval, as for example when the` machine tools have reached the limit of their cutting stroke, the main valve is automatically or manually shiftedto the op- This shifting movement may be occasioned in response to an unbalanced condition of the fluid associated with the valve. This unbalanced condition is caused by a balancing member which serves to effect the decrease in pressure of fluid at one extremity of the main valve. This unbalancing f the valve serves to carry the same past the neutral point to a position in which high pressure and low pressurefluids are delivered in a reverse direction to the machine actuating mechanisms. IThis rapid delivery., of the fluidi]-5 may continue until the machine actuating mechanisms have reached the limit of their reversing stroke, at which time the valve will be automatically or manually shifted to its neutral position. If it is desired to impart a feeding reverse movement to the actuating mechanisms, it is only v otherwords, the reversing operation will not take 'place until all of the fluid actuated mechanisms have reached/,the limit of their advancing stroke and said reversal may be very accurately controlled for each cycle of the machine operation'.

-Having presented a general description of one embodiment of the invention, I will now proceed to) more specifically describe the same in connection with the accompanying drawings, where- 1n: A

Figure 1 is an end view of my improved valve construction disclosed in operative association with an automatic lathe, certain portions of which are shown in section to more clearly illustrate thev invention;

Figure 2 is `a plan view of the dog supporting slide shown in Figure 1, the pin which is actuated by the dogs on said slide being shown in operative association therewith;

Figure 3 is a fragmentary view similar to Figure 2 disclosing an advanced position of the slide with the reversal control dog shown in abutting relation with respect to the shiftable pin;

Figure 4 is an enlarged plan view of my improved Valve i mechanism disclosed in association with fragmentary portions of a lathe, said valve being shown in section for the purpose of more clearly `illustrating the internal structure 4,thereof Figure 5.is an enlarged sectional view of the connecting pin, said view being taken substantially along the line 5 5 of Figure 4;

Figure 6 is a central vertical sectional view i of the valve mechanism taken substantially along the line 6 6 ofFigure 4;

Figure 7 is a transverse sectional view of the 'valve mechanism taken substantially along the line 7 7 of Figure 4;

Figure 8 is also a' transverse sectional view of vthe valve mechanism taken substantially along-4 the line 8 8 of Figure 4; y

Figures 9 to 12 disclose somewhat schematically various shifted positions occupied by the main valve; Figure 9 disclosing the rapid forward traverse position; Figure 10 the feeding forward position; Figure 11 the rapid reverse traverse po-V sition; and Figure 12 the feeding reverse position; Figure 13 is a fragmentary sectional view of the right end of the valve mechanism shown in 'and Figure 4 with the fluidcontrolling valve shown inthe position which it occupies when fluid is being withdrawn to effect the longitudinal shifting of the main valve;

Figure 14 is a transverse sectional View taken substantially along the line V14 14 of Figure 13;

Figure 15 is a diagrammatic representation of the fluid circuit shown in combination with my improved valve mechanism, fragmentary portions of the machine actuating mechanisms being shown in operative association with said circuit. Before discussing in detailthestructural characteristics, of the embodiment of my invention which is disclosed in the drawings, it is to be understood that" the present invention relates to subject matter similar to that set forth in my copending application, Serial No. '391,130, led

Sept. 9, 1929. In said copending application I have disclosed a complete automatic lathe construction equipped with a fluid control valve, and the present invention relates to. fluid control valves which are adapted for use in connection with such automatic lathes. However, the present-invention represents certain improvements in valve construction and controlling mechanism therefor. f

Referring to the drawings wherein like numerals have been employed to designate similar parts throughout the various figures, it will be seen that I have disclosed a main valve mechanism designatedv generally by the numeral 20 and for the purpose` of illustrating a practical application of said valve mechanism, I have disclosed the' same in association with fragmentary portions of an bautomatic lathe designated generally by the numeral 22. For` a more detailed dev scription of this automatic lathe, reference is made to my above mentioned copending application.

The valve mechanism 20 includes a housing 24 and a main cylindrical Valve denoted generally by the numeral 26 which is longitudinally reciprocable within said housing. One extremity of the housing 24 is closed by a cap `28 which provides a into an annular passage 48 whichmis provided in the housing 24. This high pressure and low pressure fluid may be supplied from any suitable sourceand for the purpose of illustrating the practical application of the valve'I have shown the same connected to a variable displacement pumping mechanism which is shown diagrammatically in Figure 15. This pumping mechanism includes a variable displacement high pressure pump designated generally by the numeral t 50 and a low pressure gear pump designated by the numeral`52. Fluid at high pressure is directed from the pump 50, Figure 15, through the pipe line 46 and thence into the annular passage 48, while fluid` at low pressure is supplied from the pump 52 through the pipe line 40 which communicates with the branch passages 42 and 44.

When the valve 26 occupies its neutral position shown in Figures 4, 6 and 15, the high pressure fluid is directed from the annular passage 48 through a valve passage 54 and thence through an annular passage 56 which at this time communicates with a chamber 58. It is also to be noted that the fluid at low pressure which i's supplied from the pipe line 40 into the branch passages 42A and 44, is `also directed into the annular passage 58.

From this passage 58 the low and high pressure pump fluid passes through radial ports 60 which communicate at their inner extremity with a longitudinal-internal passage 62. This passage.

62 Lcommunicates with an annular passage '64, Figure 6, through radial ports 66, and the passage 64 communicates with a chamber 68 at the left extremity of the housing 24, Figure 6, through an elongated passage 70. The annular passage 64, as shown in Figures 4 and 15, also communicates with the chamber 38 at the right extremity of the housing by means of a passage 72. Communication between this passage 'I2 and the' -nisn 102 with the annular passage 56, as clea'rly chamber 38 is controlled by means of an oscillatory member 74, and when the valve occupies the position shown in Figures 4 and 6, a. valve port 76 permits fluid to pass from thev passage 72 into the chamber 38. From the foregoing it will be apparent that fluid pressure is applied with substantially equal intensity at both extremities of the valve and hence said valve is in balance. The presence of the rod within the chamber 68 obviously p esents a slight variation in the surface area ac ed upon by the fluid in said chamber as compared with the surface area of the valve which is acted upon by the fluid in the valve chamber 38. However, in practice, the crosssectional area of the rod 30 presents a very ksmall fraction of the total cross-sectional area of the end section 32, Figure 15. In fact, the slightl variation in the cross-sectional areas acted upon by the fluid pressure at each end of the valve is more than compensated for by the frictional resistanceoccasioned between the valve surfaces and the valve casing. Hence, it may be stated that when the fluid pressure within the end chambers 38 and 68 are equal, the valve vis in balance and will not shift until some other force acts upon the valve, such as a mechanical shifting of the valve, or until fluid pressure within the chamber 38 is relieved, thereby permitting the normal balancing pressure actingY against the opposite end of the valve to cause said valve to be suddenly urged to the right. It is to benoted that the annular passage 64 is connected with an oil reservoir 'I8 through the agency ofV a pipe- 80,`Figures 6 and 15, a relief valve 82 and -a pipe line 84. Thus', fluid at high and low pressures which is associated with the valve when said valve occupies its neutral position, circulates therethrough without being displaced for the purpose of propelling mechanisms later to be described. Charging fluid for the .plunger pump is directed from the chamber 68 through a pipe line 85 which connects with the intake side .of the plunger pump.

' Consider now that the valve 26 is manually shifted toits extreme leftposition as shown in Figure 9 through' the agency of the control lever 34. With the valve in this position, high pressure fluid from the annular passage 48 is directed through the valve passage 54 into a passage 86 and thence through a plurality of fixed orifices 88, 90 and 92, Figures 8 and 9. -f The low pressure fluid is also directed through lthe fixedY orifices 88, 90 and 92 together with the high pressure fluid. In other words, the combined high and low pressure iiuid mediums are unrestrictedly passed through these orifices and thence through suitable pipe lines 94, 96and 98.

For purposes of illustration 'I have disclosed these pipe lines in operative association with various machine actuating mechanisms. These mechanisms are similar to thosedisclosed in my above mentioned 4copending application and a fragmentary portion of these machine elements is disclosedbecause the structure thereof does not form a part of the present invention except as these parts enter into the general combination with my improved valve mechanism. Thus, the pipe line 94 connects with a valve mechanism 100 which serves to control the distribution of copending application. When a valve member 114 of the mechanism 100 is in one position. fluid will be directed into association with the cylinder 106 and when said valve occupies the position shown in Figure 15, no fluid will be directed to said cylinder.v

The pipe line 96 communicates with an actuating mechanism 116 Which includes a cylinder 118 and a piston 120. The upward movement of this piston 120 causes the tool carriage 112 to experience a swinging movementabout the axis of the bar 110. A return pipe line 122 connects the cylinder 118 with the annular passage 56 as clearly shown in Figure 15. f The pipe line 98 is connected with an actuating mechanism 124 which includes a cylinder 126 and a piston 128. 'Ihe reciprocation of this piston 128 causes the movement of the tool carriage 130 toward and away from the work (not shown). The cylinder 126 is connected by means of a return pipe .line 132 and a pipeline 134 with the annular passage 56'. Shunted, across the pipe lines 98 and 132, as clearly shown in Figure 15, is another actuating mechanism 136 which may be used for any suitable purpose such for example as the control of a clutch mechanism (not shown).

With the foregoing description of these various machine elements and the pipe lines'connected therewith.' it should be apparent that when the main valve 26 occupies the position shown in Figure 9, the combined high and low pressure fluids will be dispatched through these various pipe lines 'so' as to cause the various machine mechanisms to be moved rapidly. In other l' to effect proper movement 4of the fluid actuated A mechanisms Thus, when a plurality of orifices such as thosedisclosed in the drawings are employed, the machine tools which are propelled by the fluid actuated mechanisms, are subjected to varying resistances and consequently the pres- .sure of the fluid in the circuit must exceed the maximum necessary for propelling these machine tools in order to obtain unison in operation. Therefore it is important that the size of these fixed orifices 88, 90 and92 be gauged so as to insure proper pressure conditions and thereby enable the control of a plurality of machine tools from a single source of fluid supply and by means of a single valve. I

Consider now that the valve is shifted to the position shown in Figure 10, which position will hereinafter be referred to as the forward feed traverse position. It will vbe noted that when the valve occupies this position, the section 32 thereof closes the fixed orifices-88, 90 and'92 and sections 138 and 140 of said valve prevent the low pressure fluid from entering the passage 86.

This. lo`w pressure fiuid is diverted from the branch passages 42 and 44 through the radial ports 60 and 66 and thence into the annular passage 64 which is connected with the reservoir i' 78., The high pressure fluid, however, passes through the valve passages 54 and 86 and thence ^size )of these orifices is adjustably determined by suitable needle valves 142, 144 and 146 as clearly shown in Figure 7. These adjustable orifices 88a, 90a and 92a areA companion with the above mentioned fixed orifices 88, 90 and 92 respectively, and it will be seen that the adjustable as well as the xed orices communicate respectively with the pipe lines 94, 96 and 98. Thus,

when the valve 26 occupies the position shown in Figure 10, high pressure uid will be directed through the restricted orradjustable orifices and 6 thence into the various pipe lines which are connected with the actuating mechanisms.

restricted orifices may be adjusted to permit any desired displacement of the fluid, this displacement being employed to effect a forward feeding stroke to thepistons in the actuating mechanisms.` In other Words, when the valve occupies the position shown in'Figure 10, uid will be distributed to the various actuating mechanisms at a feeding displacement as distinguished from the increased displacement which takes place in the manner described above in connection with the forward rapid traverse position of the valve (Figure 9). It is to be noted that the fluid supplying mechanism or pump shown in the drawings is of the type which may be varied to increase or decrease the displacement of fluid. Thus, by the restricted adjustable orices 88a, 90a and 92e, I am able to adjust these orifices in accordance with the speed at which uid is displaced by the rotary'plunger pump. In this manner I am able to positively\control the speed of .travel of the 40 fluid actuated mechanism to which each of said adjustable orifices is connected.

Consider now that the control leve;` 34 is swung from its forward feed position past the neutral point to its extremeposition to the right.' This will position the valve as'shown in Figure 11. With the valve in this position., the combined high pressure and low pressure fiuids are directed through the valve passages 54 and thence outwardly in a reverse direction through the pipe lines 105, 122 and 134. That is to Say, the high and low pressure iiuids are displaced in a reverse direction so as to cause a rapid reverse movement of the various actuating mechanisms. The pipe lines 94, 96 and 98, under these circumstances, serve as return conduits and direct the fluid medium through the fixed orifices 88, 90 and 92 and thence into the valve chamber 68.` Fluid from this chamber 68 is directed through ithe passage 70, Figure 6, and thence into the annular passage 64 which is connected by the return pipe 80 to the reservoir 78.

as shown in Figure 11 will hereinafter be referred to asthe rapid reverse position. By returning 65 shown in Figure 4, both high pressure and low through adjustable orifices 88a, 90a and 92a. The,

These The position of the valve` the control lever 34 to its neutral ,position as #the sections 138 and 140 of the valve prevent the i low pressure fluid from entering the valve passages 54. The high pressure fluid, however, is directed through the return pipe lines and fluid is forced in a reverse direction through the adjustable orifices 88a, 90a and 92a. Passing the uid through these vadjustable orifices causesa decrease in displacement and thereby enables the pistons of the actuating mechanisms to be moved in a reverse direction at a feeding speed. The position of the valve shown in Figure 12 will be hereinafter referred to fas the feeding reverse position.

From theforegoing't will be apparent that my improved valve may be shifted to five different positions Within its housing through the agency 4of a manually operabledever. If-will now proceed to describe the mechanism for automatically effecting the shifting of said valve. 'Ihis mechanism includes a Aslide 148 which is connected to one extremity of 'a rack bar 150, Figs. l to 4 inelusive. Movement of the rack bar and slide to the left, Fig. 2, is occasioned in response to the forward movement of the tool carriage shown in Figure 15. Assume that the control lever 34 has been manually moved from the neutral position shown in Figure 4 to its extreme left position so as to shift the valve tothe position shown in Figure 9. This will obviously effect rapid forward movement of the pistons 120 and 128. The forward movement of the carriage 130 causes the movement of the rack bar through the agency of suitable gears 152, 154 and 156. For a more detailed disclosure of this arrangement reference is again made to my above mentioned copen'ding application. The slide 148 carries a plurality of adjustably positioned dogs 158, 160 and 162. The dog 158 is positioned on the slide so as to engage an arm 164 of a bell-crank 166, Figure4 4, at a proper predetermined interval during the cycle of operation of the machine or lathe 22. In other words,after the carriage tool 112, Figure 15, has vbeen swung to a predetermined position, the-dog, 158 engages the arm 164 and causes the valvelmember 114 to be shifted to the left as shown by the dot and dash lines, Figures 4 and 15. This establishes communication between the supply pipe 94v and the pipe104 which connects with the actuating mechanism 102. Longitudinal movement to the left is thus imparted to the bar 110.

\At a predetermined interval during the advancing movement of the slide 148, the dog 160 is carriedvintjo engagement with a pin 170 which depends from and Lis supported at the outer" extremity of a slide bar 172 whichis slidably mounted within a suitable frame 174. This slide bar 172 is detachably connected with one extremity of a link 176 by means of a removable pin 178, Figures 4 and 5. The opposite extremity of thelink 1 76 is pivoted to the control lever 34'and thus any longitudinal movement experienced byl the link 176 andgthe slide bar 172 willbe transmitted to the main valve 26. The engagement ofthe dog 160 with the pin 170 causes said pin to be 140 positively shifted to the right, Figure 4,4 so asto automatically cause the main valve to be shifted i to the forward feed traverse position shown in Figure 10. -As already described', the valve this positon causes fluid to be displaced at a feeding rate to the Various actuatingmechanisms. In order to more readily understand the co-action between the dogs and the pin 170, Lhave shownby dotted lines in Figures 2 and 4, the various shifted positions occupied by the pin 170 and 150 these positions are denoted by the letters A, B, C and D. Thus, the dog 160 shifts the in'170 from the position A to theposition B. the slide 148 continues to advance, a block 180 adjustably positioned on said slide, is moved forwardly and an abutment surface 182 of Vsaid block is moved across or in front of the adjacent surface of the pin 170 as clearly shownin Figure 3. In this position the abutment surface 182 will prevent longitudinal movement of the slide bar 172 to the right, Figs.,3 Iand 4. The abutment surface of this block 180 co-operates with a mechanism 184.

Figures l and 4, about to be described so as to positively and accurately control the shifting of the main valve 26.

This mechanism 184 includes a lever arm 186 lwhich is secured to the upper extremity of a vertical pin 188, and an arm 190 secured to the lower end of said pin. This arm 190 is adapted to be engaged by a lug-192, Figure 15, which moves with the horizontal bar 110. For purposes of illustration this lug is shown in dot and dash lines in Figures 1 and 4. Ihis lug 192 engages the arm 190 when the carriage 112 reaches the limit of its movement to the left in response tofthe actuation of the mechanism 102. This causes a link 194 connected to the arm'186 to be urged to the left, Figure 1, against the action'of a coil spring 198. The outer extremity of the link 194 is provided with rack teeth which mesh with a pinion 198 secured to one extremity of a shaft 200iy The opposite extremity of this shaft 200 carries the oscillatory member 74. From the foregoing it will be apparent that when/the arm 190 is actuated, partial rotation will be imparted to the valve 74 'so as to move a port 202 to the position shown in Figure 13. When the valve 74 is rotated to this lposition, communication between the passage 72 and the chamber 38 will be interrupted and communication will be established between said chamber and a return pipe 204 which is connected with the reservior 78. Thus, fluid will be immediately displaced from the chamber 38, thereby unbalancing the fluid pressure to which the valve is subjected. If, at the time the valve 74 is rotated to the fluid displacement position shown in Figures 13 and 14, the abutment surface 182 has been carried beyond thel pin 170, the main valve 26 will immediately be shifted to the right, Figure 4, in view of the unbalanced fluid pressure.V It will thus be apparent that the shifting of the valve for the purpose of reversing the flow of the fluid medium is controlled by the last tool carriage toA reach the limit of its forward movement. By employing the abutment surface 182, the reversal of the fluid may be controlled with a high degree of accuracy and this is very important in connectionA with the operation of a machine such as an automatic lathe wherein a plurality of tool carriages are employed. In such instances the period of reversal of the carriages should be accurately controlled and the arrangement just described makes possible such control.

From the foregoing it will be apparent that when the main valve 26 is shifted in response to the unbalancing of the fluid pressure, the pin 170 is carried to the dot and dash position which is designated by the letter C in Figures 2 and 4. As the dog 158 approaches the limit of its rearward movement, it will be carried into engagement with the arm 206 of the bell-crank 166, thereby causing the valve, 114 to cut off the supply of fluid to the actuating mechanism associated with the bar 110,I Figure l5. The cam surface of the dog '162 is eventually carried into engagement with the pin 170, thereby moving the pin from the position C to the neutral position shown by the solid lines in Figures 2 and 4. In this manner the main valve 26 is shifted to its neutral position, thereby arresting the dispatching of fluid to the actuating mechanisms. -In Vorder to complete a subsequent cycle of operation it is only necessary tov move the control lever 34 to the left as above described. In instances where it is desirable to have the actuating mechanisms operated to a reverse feeding speed, it is only necessary to include another dog (not shown) on the slide between the dogs 160 and 162 which will cause the pin 170 to be shifted to the position D shown in Figures 2 and 4.

Attention is directed to the structure shown in Figure 5 of the drawings. In thisl figure I have shown in detail the arrangement of the pin 178 1 which serves to connect the link 176 with the shifter bar 172. A spring pressed plunger 208 isl mounted-within the slide bar and is adapted to yieldingly interlock with a V-shaped groove 210 formed in the pin 178. To disconnect the link and slide bar it is only necessary to exert an upward pull on the piny 178 which is suilicient to counter- 100 act the yieldable locking action of the plunger 208. The advantage of this type of connection will be readily apparent when it is understood that the valve is rendered manually controllable when the link and shifter bar aredisconnected. 105 It may be desirous, for example in some instances, to manually control the main valve 26 when the machine with which it is associated is being set up for a particular job. After the machine has been adjusted for a complete cycle of operation, y

the pin 178 may be inserted, thereby rendering the actuation of the valve completely automatic with the exception, of course, of the initial manual movement of the control lever 34.

summarizing the foregoing description, it will be understood that in the operation of my improved valve mechanism, the dogs on the slide 148 are first positioned in accordance with the various shifting movements which are to be experienced by the tool carriages or other movable elements .with which the valve is associated. After these dogs have been properly positioned and the work set up in the machine, the control lever 34 is shifted to its extreme left position, Figure 4, so as to move the valve 26 from its neutral position shown in Figure 4 to its rapid approach or forward position shown in Figure 9. In this position fluid-at high pressure from the pipe line 46 enters the annular passage 48 and is 30 directed through the valve passages 54, the pas- '1 sage 86 and thence through the orifices 88, 90 and 92.l The low pressure fluid is directed from the pipe line 40 and passes through the branch passage `42 and joins the high pressure fluid in the passage` 86. From this point is is introduced within the or-iflces. From these orifices the combined fluid is displaced through the pipe lines 94, 96 and 98 which are connected with the actuating mechanisms. The increased displacement resulting .from the combination of the highland low pressure fluids causes these actuating .mechanisms to be moved at relatively high speeds. The movement of the carriage causes the slide 148 to be actuated, and the dog 160 carried thereby is eventually moved into engagement with the pin 170. This causes the 'shifting of said pin from the position A to the position B shown in Figure 4Q The valve 26'is thus moved to the forward or approach feeding position 150 shown in Figure 10. The high pressure fluid alone vis then directed through the adjustable orifices 8825'90a and 92a thereby causing the actuating mechanisms `tfo be moved at a feeding speed.

The dog 158 engages the arm 164 of the bellcrank` 166 and this causes communication to be established between the pipe lines 94 and 104 as clearly shown in Figure 4. As the various tool carriages approach the limit of their approach or advancing movement, the lug 192 is carried into engagement with the arm 190 and this causes they bar 194 to be shifted, thereby causing rotation of the member 74. The port 202 of the member l74 is thus carried into registration with the pipe line 204 and fluid from the chamber 38 is dispatched through said pipe line and into the reservoir '18. If the abutment surface 182 of the block has been moved past the pin 170, the valve 26 will be moved to the right, Figure 4, as a result of the unbalancing of the fluid pressure. The valve is thus carried to the position shown in Figure 11 and at this time the combined low and high pressure fluids will be dispatched in.I a reverse direction through the pipe lines, said fluid being returned to the chamber 68 through the unrestricted orifices. ment causes rapid reverse movement of the actuating mechanisms and as the slide 148 continues to move rearwardly, the dog 158 engages the bellcrank arm 206 so as to shift the valve 114. The dog 162 is eventually carried into engagement with the pin 170, thereby causing said pin to be moved from the position C to the neutral solid line position shown in Figure 4. Additional dogs may be provided if it is desired to cause the valve to be moved to its feeding reverse position shown in Figure 12. i

From the foregoing it will be apparent that my invention contemplates the .provision of a Valve mechanism of improved practical construction in which increased displacement of the fluid medium is accomplished by combining high pressure and low pressure fluids. This is accomplished by the simple and unique arrangement of the passages in the valve mechanism. One of the distinct advantages of my present invention resides in the manner in which the-valve is shifted to its reverse position in response to the unbalancing of the uid pressures to which it is subjected. This is accomplished in a very simple 'and expeditious manner. Another feature which represents a decided improvement in valve construction is the manner `in which I directly associate the xed and adjustable orifices with the valve housing. By this arrangement no auxiliary units are needed and the entire valve mechanism is rendered self-contained in every respect. It is` also to be noted that I employ the restricted or adjustable orifices for effecting the delivery of fluid at a feeding .rate in both forward and reverse directions. By means of the abutment surface 182 which co-operates with the mechanism for oscillating the member 74, a distinct improvement is presented in that I am able to positively and accurately control the period of reversal of fluid flow. 'Ihis problem of accurately controlling the reversal of fluid .valves has been one which has confronted those interested in this particular art for some time. To my knowledge, no accurately operable control mechanism has thus far been developed and therefore I believe that my present arrangement represents'an improvement long sought for in this particular art.'

As pointed out above, the valve may be rendered manually operable by simply withdrawing a connectory pin and this greatly facilitates the ease This increased displacewith which a machine may be set up. The connection may be establishedI with equal ease by merely reinserting the pin so as to render the valve completely automatic in operation. As shown in the diagrammatic representation of Figure 15, I employ suitable relief valves in association with the fluid circuit so as to positively preclude the building up of pressures to an extent which would tend to cause damage to any of 'the operating parts. representation I have also disclosed a tail stock device which is indicated generally by the numeral`i212. This is merely disclosed to Ishow the practical application of my improved valve mechanism with an automatic lathe or machine oi hke nature. It should also be notedv that intermittent movement pf'the machine toolsy may be In this diagrammatic plished byvsimply' employing additional dogs on the slide 148. I

While I have disclosed'particular types of machine parts and a particular type of fluid pumping mechanism .in association with the valve mechanism, it should be clearly understood that my invention is not limited to the specific application shown in lthe drawings; but is capable of being used in combination with numerous other types of devices wherein fluid is employed as a propelling medium. In other words, the uid pumping devices 50 and 52 and the automatic lathe 22 shown in the drawings are merely for illustrative purposes and should not in any sense limit the broad application of my improved valve mechanism.

Having thus described my invention, what I claim as new and desire vto secure by Letters Pat- Aent is:

' l. A vvalve construction lincluding a housing, a unitary valve shiftable within said housing, said valve and housing having cooperative passages for variously directing fluid, said housing having a fluid dispatching orifice, means for introducing fluid at a given pressure into association with said valve, and another means for introducing fluid at another given pressure into association with said valve, the disposition of the passages in said housing and valve being such as to direct both of said introduced fluid mediums through said fluid dispatching orifice when the valve occupies a given shifted position, and to direct only one of said fluids through said orifice when the valve occupies another shifted 'posif the valve occupies/a predetermined shifted position to permit of increased fluid isplacement, and to direct iiuid to only the resv ricted orifice when said valve occupies another shifted position to permit of decreased fluid displacement.

y 3. A valve construction including a housing and a valve shiftable Within said housing, said valve and housing having cooperative passages for simultaneously receiving at least twov fluid mediums at different pressures and to variously direct said fluid, said'passages being adapted to Y communicate with( a restricted orifice and anvfor directing fluid at a given pressure into association with said valve, and another means for directing fluid at another given pressure into association With said valve, the passages in said valve and housing being such as to direct both of said introduced fluids to the fixed orifice when the valve occupies a given shifted position, and to direct fluid to said adjustable orifice when the valve occupies another shifted position.

5. A valve construction including a housing, a shiftable valve in said housing, said valve and housing having cooperative passages for variously directing fluid, means for directing a fluid medium into association with said valve, said passages being associated with a restricted orificeand another unrestricted orifice, said passages being disposed soas to direct fluid to the second mentioned orifice when the valve occupies one shifted position to permit of increased fluid displacement, and to close said second orifice and direct fluid to the restricted orifice when the valve occupies another shifted position to permit of decreased uid displacement.

6. A valve construction including a housing, a shiftablevalve in said housing, said valve and housing having cooperative passages for simultaneously receiving at least two fluid mediums at different pressures and to variously direct said fluid, said valve when in one shifted position serving to dispatch a fluid medium in a given direction, and when in another shifted position to dispatch said fluidin a reverse direction, chambers associated with said valve for receiving fluid to balance said valve, and means for relieving fluid pressure in one of said chambers to unbalance the fluid pressure on said valve and thereby effect the shifting of the valve from one position to another in response to the pressure of the balancing fluid in the other chamber.

7. A valve construction including a housing, a shiftable valve in said housing, said valve and housing having cooperative passages for simultaneously receiving at least two fluid mediums at different pressures and to variously direct said fluid medium, said valve being adapted in one shifted position, to effect the delivery of fluid in a given direction and when in another shifted position, to'efect the delivery of fluid in another direction, a pair of spaced chambers for receiving fluid to balance said valve, and means for relieving fluid pressure in one of said chambers to thereby unbalance fluid pressure and cause said valve to be shifted 'from one position to another in response to the pressure of the balancing fluid in the other chamber.

8. A valve construction including a housing, a

Ashiftable valve in said housing, said valve and housing having cooperative passages for variously directing a fluid medium, said valve being adapted in one shifted position, to effect the delivery of fluid in a given direction and when in another shifted position, to effect the delivery of fluid in another direction, a pair of spaced charnbers, said chambers communicating-With each other through a passageway whereby fluid pressure in one chamber will be substantially equal to thefluid pressure in the other chamber, and means.. for withdrawing fluid from one of said chambers, whereby said valve will be automatically shifted from one position to another.

9. A valve construction including a housing, a shiftable valve in said housing, said valve. and housing having cooperative passages for variously directing fluid, said valve being adapted in one shifted position, to effectthe delivery of fluid in a given direction and when in another shifted position, to effect. the delivery of fluid in another direction,.. a chamber at each extremity of said valve for receiving fluid, said chambers being connected by means of a passageway, and a mechanism for effecting the withdrawal of fluid from one of said chambers to cause said valve member to be shifted ,from one position to an,- other.

10. A valve construction including a housing, and a reversing valve shiftable Within said housing, said valve and housing having cooperative L passages for directing fluid to either end of a hydraulic actuator, a restricted orice, and another larger orice to permit of increased fluid displacement, said orifices beingy included within said housing and adapted to receive fluid discharged l from an actuator to which said valve may be connected in accordance with various shifted positions of said valve within said housing.

ll. A valve construction including a housing,

and a shiftable reversing valve in said housing,

said valve and housing having cooperative passages for directing fluid to either end of a hy draulic actuator, a restricted orifice and another larger orifice to permit of increased fluid displacement, said orifices being provided within said housing and adapted to receive fluid discharged from the actuator with which said valve may be connected, said valve serving when in one position to open one of said orifices and when in another position to close one of said orifices.

l2. In combination with a fluid actuated means, a valve mechanism for controlling the delivery of fluid to said fluid actuated means, said valve mechanism including a housing and a valve shiftable within said housing, said valve and housing havingA cooperative passages, said valve being adapted in one shifted position vto effect the delivery of fluid in a given direction to said fluid actuated means and when in another shifted position to effect-the delivery of fluid in a reverse of fluid in a given direction to said fluid actuated means and when in Aanother shifted position, to

effect the delivery of uid in a reverse direction, means for conditioning said valve to be shifted to its reverse position, and abutment means for preventing the longitudinal shifting of the valve to said reverse position until said fluid actuated mechanism has completed a predetermined cycle of operation.

14. In combination with a fluid actuated means, a valve mechanism for controlling the delivery of fluid to said fluid actuated means, said valve mechanism including a housing and a valve shiftable within said housing, said valve and housing being provided with cooperative passages for variously directing a fluid medium, said valve being adapted in one shifted position to effect the delivery of fluid in a given direction to said fluid actuated means and when in another shifted position to effect the delivery of fluid in a reverse direction, shiftable means operatively connected with said valve, and means providing a stop for engaging said shiftable means to prevent the shifting of the valve in a given direction.

15. In combination with a fluid actuated means, a valve mechanism for controlling the delivery of fluid to said fluid actuated means, said valve mechanism including a housing and a valve shiftable Within said housing, said valve and housing being provided with cooperative passages for variously directing a fluid medium, said valve being adapted in one shifted position to effect the delivery of fluid in a given direction to said fluid actuated means and when in another shifted position to effect the delivery of fluid in a reverse direction, shiftable means operatively connected with said Valve, and a shiftable stop for engaging said shiftable means to prevent the shifting movement of the valve in a given direction.

16. In combination with a fluid actuated means, a valve mechanism for controlling the delivery of fluid to said fluid actuated means, said valve mechanism including a housing and a valve shiftable Within said housing, said valve and housing being provided with cooperative passages for variously directing a fluid medium, said valve being adapted in one shifted position to effect the delivery of fluid in a given direction to said fluid actuated means and when in another shifted position to effect the delivery of fluid in a reverse direction, a slide, and an abutment means carried by said slide to prevent the shifting of said valve in a given direction.

17. In combination with a plurality of fluid actuated mechanisms, a valve mechanism for controlling the delivery of fluid to said fluid actuated mechanisms, saidmvalve mechanism including a valve shiftable Within a housing, said valve being adapted inone shifted position to effect the delivery of fluid in a given direction and when in another shifted position to effect the delivery of fluid in another direction, means for controlling the shifting of 'the valve Within its housing, said control means being operable inv response to the actuation of one of said fluid actuated mechanisms, and an abutment means movable in response to the actuation of one of said fluid actuated mechanisms for temporarily preventing the shifting of said valve mechanism.

18. 4In combination with a plurality of fluid actuated mechanisms, a valve mechanism for controlling the delivery of fluid to said fluid actuated mechanisms, said valve mechanism including a valve shiftable Within a housing, said valve being adapted in one shifted position to effect the delivery of fluid in a given direction and When in another shifted position to effect the delivery of fluid in another direction, means for controlling the shifting of the valve within its housing, said control means being operable in -response to the actuation of one of said fluid actuated mechanisms, means movable in response to the actuation of one of said fluid actuated mechanisms, and an abutment means carried by said movable means which is adapted to temporarily prevent the shifting of said valve within its housing.

19. In combination with a plurality of fluid actuated mechanisms, a valve mechanism for controlling the delivery of fluid to said fluid actuated mechanisms, said valve mechanism including a valve shiftable within a housing, said valve, when in one position, being adapted to effect the delivery of fluid in a given direction and when in another shifted position to effect the delivery of fluid in another direction, said valve being shiftable in a given direction by fluid pressure, means operable in response to the actuation of one of said fluid actuated mechanisms for unbalancing the fluid pressure in said valve to effect the shifting thereof, and a shiftable abutment means for temporarily preventing the shifting of said valve, said abutment means being shiftable in response to the actuation of one of said fluid operated mechanisms.

20. In combination with a plurality of fluid actuated mechanisms, a valve mechanism for controlling the delivery of fluid to said fluid actuated mechanisms, said valve mechanism including a valve shiftable Within a housing, said valve when in one position being adapted to effect the delivery of fluid'in a given direction and when in another position to effect the delivery of fluid in another direction, a slide operable in response, to the actuation of one of said fluid actuating mechanisms, and an abutment member adjustably mounted on said slide for temporarily-preventing the shifting of said valve.

21. In an apparatus of the class described, a fluid control valve including a valve shiftable Within a housing for variously controlling the flow of a fluid medium, `manually operable means at one'extremity of said valve for effecting the shifting of said valve Within its housing, means for automatically shifting said manually operable means, and a detachable coupling for rendering the automatic control means functionally inoperative.

lmechanism With said shiftable machine element,

and a detachable connector for rendering the automatic functioning of the machine element ineffective Whereby to enablecomplete manual control of the valve mechanism.

23. A valve construction including a housing, a unitary valve shiftable Within said housing, said valve and housing having cooperative passages for variously directing a fluid medium, said valve being adapted to receive fluid from a plurality of sources and when in one shifted position, to effect the dispatching of fluid from one of said sources and when in another shifted position, to receive lli) and effect the dispatching of combined fluids from said sources, the communication with saidsources being maintained during the shifting of `said valve.

24. In combination .with a plurality of fluid actuated mechanisms for propelling machine parts and a plurality of fluid pumping devices; a valve mechanism for controlling the distribution of fluid to said fluid actuated mechanisms, said valve mechanism including a unitary valve shiftable Within a' housing, said valve being adapted when in oneV position to receive and effect Ithe distribution of fluid supplied thereto from one of said sources, and when in anotherposition, to receive and effect the distribution of the combined fluids from said sources, and Ameans for shifting said valve, said means being shiftable in response to the actuation of said fluid actuated mechanisms. y

25. In combination with a fluid actuated mechanism for propelling machine elements and the like and a lplurality of fluid supplying devices, a valve construction 'including a unitary valve member shiftable Within a housing, said valve having an orifice which is of a size corresponding to the fluid displacement requirements of the uid actuated mechanism so as to effect uniform delivery to said mechanism, said valve when in one position being adapted to effect the delivery of fluid from one of said sources of supply to said fluid actuated mechanism, and when in another shifted position, to effect the delivery of combined fluids from said sources through said gauged orifice to saidfluid actuated mechanism..

26. In combination with a plurality of fluid actuated mechanisms for propelling machine elements and the like and a plurality of fluid supplying devices, a valve mechanism including a valve shiftable within a housing, said valve having a plurality of gauged orifices, each of said orifices being connected with one of said fluid actuated mechanisms, said orifices being of a size which corresponds to the operating characteristics of the fluid actuated mechanisms whereby to obtain uniform displacement to said mechanisms, said valve when in one position being adapted to receive and displace fluidfrom one of said fluid supplying devices to said fluid actuated mechanisms and when in another shifted position, to effect the displacement of 'combined fluids from said sources through said gauged orifices.

27. A valve construction including a housing, a shiftable valve in said housing, said valve and vhousing having cooperative passages for variously directing a fluid medium, said valve being adapted when in one shifted position to effect the delivery of fluid in a given direction, and when in another shifted position to effect the delivery of fluid in another direction, chambers in said housing for receiving fluid to substantially balance said shiftable valve,'and means operable independently of the valve for relieving fluid pressure in one of said chambers, whereby to effect the automatic shifting of the valve in response to the normal balancing pressure of the fluid in the other chamber.

28. In combination with a fluid actuator, a valve mechanism' for controlling the delivery of fluid to said actuator, said valve mechanism including a housing and a valve member shiftable within said housing,- said valve and housing being provided with cooperative passages for vaa low pressure pump connected with said valve at a point spaced from said first connection, said valve and housing having cooperative passagesl whereby fluid from both of said pumps may be directed to a common point, and whereby, in a shifted position of said valve, the fluid from the variable displacement pump is directed to one' point and the fluid from the other pump to another point. f"

29. A valve construction including a housing, a cylindrical type valve member longitudinally shiftable within said housing, said valve and housing having cooperative passages for variously directing fluid, chambers in said valve mechanism for receiving fluid to maintain said valve member in balance, and means at one extremity of said housing for relieving fluid from one of said chambersto thereby enable the balancing fluid in the other chamber to effect the sudden longitudinal shifting of said valve member. 30. A valve construction including a housing, a cylindrical type valve longitudinally shiftable within said housing, said valve and housing having cooperative passages for variously directing fluid, a plurality of chambers for receiving fluid to maintain said valve in balance, and means associated as a unit with said housing for relieving fluid from one of said chambers to render the fluid in the other chamber operable for longitudinally shifting the valve.

31. A valve construction, including a housing, a valve member shiftable within said housing, said valve and housing having cooperative passages for variously directing fluid, a plurality of chambers for receiving balancing fluid which is operable during the shifting of the valve member from one position to another in a given direction, and means for effecting the unbalancing of said valve to cause said valve to be suddenly shifted in the opposite direction.

32. In combination with a hydraulic actuator system including a source of relatively high pressure fluidY supply, a source of relatively low preslivery of fluid from said 10W and high pressure fluid supplies to said actuator, chambers in said valve housing for receiving low pressure fluid to maintain the valve inA balance, and means for relieving fluid from one of said chambers to thereby unbalance fluid pressure so as to cause said valve to be shifted from one position to another in response to the low pressure balancing fluid in the other chamber.

33.In combination with a hydraulic actuator for propelling machine parts and the like which includes a cylinder and piston construction, pumping means for delivering fluid for propelling purposes to said actuator, and a unitary fluid control means ,including arestricted orifice for receiving fluid discharged from said actuator during the feeding movement thereof in a given direction, means for rendering said restricted oriflce functionally, ineffective whenthe actuator is moving at a faster rate in the same direction, and means for directing fluid to either end of said actuator.

for propelling machine parts andthe like which includes a cylinder and piston construction, a relatively low pressure pump for delivering fluid at a relatively rapid rate to said actuator, a relatively high pressure pump for delivering fluid at a slower feeding rate to said actuator, fluid control means including a restricted orifice for receiving fluid discharged from said actuator during the feeding movement thereof in a given relatively low pressure pump for delivering fluid at at relatively rapid rate to said actuator, a relatively high-pressure pump for delivering fluid at a slower feeding rate to said actuator; fluid control means including a restricted orifice .for receiving fluid discharged from said actuator during the feeding movement thereof in a given direction, means for rendering said restricted ori- -fice functionally ineffective when the actuator moves at a fasterrate in the same direction, and a relief valve connected with the discharge side of at least one of said pumps.

36. In combination with a hydraulic actuator for propelling machine parts and the like which includes a cylinder and piston construction,I a-

relatively low pressure pump for delivering fluid at a relatively rapid rate to said actuator, a relatively high-pressure pump for delivering fluid at a slower feeding rate to said actuator, fluid control means including a restricted orifice for receiving fluid discharged from said actuator during the feeding movement thereof in a given direction, a relief valve connected` with the discharge side of at least one of said pumps, and means for controlling the delivery of fluid to either end of said actuator.

37. In combination with a hydraulic actuator for propelling machine parts and the like which includes a cylinder and piston construction, a rapid traverse pump for delivering propelling fluid to said actuator, a feed pump for delivering propelling fluid to said actuator, fluid control means including a restricted orice for receiving fluid discharged from said actuator when said actuator moves at a feeding rate, a less restricted orifice for receiving fluid discharged from said actuator when said actuator moves at a faster rate, means for controllingthe operative functioning of said orifices, and means for directing fluid to either end of said actuator.

38. In combination with a hydraulic actuator vfor propellingmachine parts and the like which includes a ,cylinder and piston construction,

pumping means for delivering fluid under presincludes a cylinder and piston construction, a

rapid traverse pump fordelivering fluid to said actuator, a'feed pump for delivering fluid to said vthereby render the balancing fluidin another actuator, fluid control means including a re'- stricted orifice for receiving fluid discharged from said actuator when said actuator moves at a feeding rate, and aless restricted orifice for receiving fluid discharged from said actuator when said actuator moves at a faster rate,.and means for selectively controlling the operative functioning `of'said orifices whereby 'when the fluid passes through the less restricted orifice the actuator will experience rapid traverse rate and when said fluid passes through the otherorifice said actuator will experience a feeding rate of travel.

40. In combination with a hydraulic'actuator for propelling machine parts and the like which includes a cylinder -and piston construction, pumping means for delivering fluid under pressure -for propelling purposes to said actuator, and a unitary fluidV control means including an adjustable restricted. orifice for, receiving fluid discharged from said actuator when said-actuator movesat a feeding rate, a less restricted orice for receiving fluid discharged from said actuator when said actuator moves at a faster rate, and means for 'controlling the operative functioning of said orifices.

41. In combination with a hydraulic actuator kfor propelling machine parts and the like which includes a cylinder and piston construction, a rapid traverse pump for delivering fluidl to said actuator, a feed pump for delivering fluid to said actuator, fluid control means including a -ref stricted orifice for receiving fluid discharged. from said actuator when said actuator moves at a feeding rate, and a less restricted orifice for receiving fluid discharged'from said actuator when said actuator moves at a faster rate, and shiftable valve means for closing the less restricted orifice to render the other orifice functionally operable to receive fluid discharged from said actuator, said valve means in another shifted position serving to open said less restricted orifice and thereby render the same functionally operable to receive fluid discharged from said actuator.

42. A fluid control mechanism including a 20 housing, a cylindrical 'type valve longitudinally shiftable within said housing, said valve and housing having cooperative passages for variously directing fluid, a plurality of chambers for reof said chambers operable for longitudinally 1`30 shifting the valve.

43. A fluid control mechanism including a housing, a, cylindrical type valve longitudinally shiftable within said housing to at least five positions, said valve and housing having cooperative passages for variously directing fluid, a plurality of chambers 4for receiving fluid under pressure to maintain said valve in balance, and shiftable means having a fluid conducting passage adapted when shifted to a given position to effect the withdrawal of fluid from at least one of said chambers and thereby render the balancing fluid in another of said chambers operable for longitudinally shifting the valve;

ERNEST J. SVENSON.

DISCLAIMER 1,924,422.-Ernest J. Swenson, Rockford, 111. VALVE CoNsTRUeTIoN. Patent dated August 29, 1933. Disclaimer filed September 24, 1943, by the assignee,

Odin Corporation. Hereby enters this disclaimer to claims 5, 8, 9, 10, 11, 23, 25, 33, 34, 35, 36, 37, 38, 39, 40 and 41.

[Oficial Gazette October 26', 1.943.] 

